CN114103906B - Parking brake device for vehicle - Google Patents

Parking brake device for vehicle Download PDF

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Publication number
CN114103906B
CN114103906B CN202011344773.3A CN202011344773A CN114103906B CN 114103906 B CN114103906 B CN 114103906B CN 202011344773 A CN202011344773 A CN 202011344773A CN 114103906 B CN114103906 B CN 114103906B
Authority
CN
China
Prior art keywords
gear
transmission gear
transmission
gear member
unit
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN202011344773.3A
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Chinese (zh)
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CN114103906A (en
Inventor
崔无尽
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hyundai Mobis Co Ltd
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Hyundai Mobis Co Ltd
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Filing date
Publication date
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Publication of CN114103906A publication Critical patent/CN114103906A/en
Application granted granted Critical
Publication of CN114103906B publication Critical patent/CN114103906B/en
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/74—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with electrical assistance or drive
    • B60T13/746—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with electrical assistance or drive and mechanical transmission of the braking action
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
    • F16D65/183—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes with force-transmitting members arranged side by side acting on a spot type force-applying member
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/74—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with electrical assistance or drive
    • B60T13/741—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with electrical assistance or drive acting on an ultimate actuator
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T1/00—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles
    • B60T1/02—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels
    • B60T1/06—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels
    • B60T1/065—Arrangements of braking elements, i.e. of those parts where braking effect occurs specially for vehicles acting by retarding wheels acting otherwise than on tread, e.g. employing rim, drum, disc, or transmission or on double wheels employing disc
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F16D55/225—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads
    • F16D55/226—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members the braking members being brake pads in which the common actuating member is moved axially, e.g. floating caliper disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
    • F16H1/206—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members characterised by the driving or driven member being composed of two or more gear wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/2809—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/065—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with a plurality of driving or driven shafts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2400/00—Special features of vehicle units
    • B60Y2400/60—Electric Machines, e.g. motors or generators
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2400/00—Special features of vehicle units
    • B60Y2400/70—Gearings
    • B60Y2400/73—Planetary gearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/18—Electric or magnetic
    • F16D2121/24—Electric or magnetic using motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/34—Mechanical mechanisms converting rotation to linear movement or vice versa acting in the direction of the axis of rotation
    • F16D2125/40—Screw-and-nut
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/44—Mechanical mechanisms transmitting rotation
    • F16D2125/46—Rotating members in mutual engagement
    • F16D2125/48—Rotating members in mutual engagement with parallel stationary axes, e.g. spur gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/44—Mechanical mechanisms transmitting rotation
    • F16D2125/46—Rotating members in mutual engagement
    • F16D2125/50—Rotating members in mutual engagement with parallel non-stationary axes, e.g. planetary gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
    • F16H1/22—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H2001/2881—Toothed gearings for conveying rotary motion with gears having orbital motion comprising two axially spaced central gears, i.e. ring or sun gear, engaged by at least one common orbital gear wherein one of the central gears is forming the output
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • F16H2001/327—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear with orbital gear sets comprising an internally toothed ring gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2702/00—Combinations of two or more transmissions
    • F16H2702/02—Mechanical transmissions with planetary gearing combined with one or more other mechanical transmissions

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transportation (AREA)
  • Braking Arrangements (AREA)
  • Retarders (AREA)

Abstract

A parking brake apparatus for a vehicle, comprising: a motor part that receives electric power from the outside and generates power; a power transmission member rotated by driving of the motor member; a pair of pressing units that receive power from the power transmission member and press the brake pads; a load transfer unit that is installed between the pair of pressing units, is connected to each of the pair of pressing units, and transfers a pressing load of any one of the pair of pressing units to the other pressing unit; and a transmission gear member restraining unit that selectively restrains driving of the load transmitting unit in conjunction with rotation of the power transmitting member.

Description

Parking brake device for vehicle
Technical Field
Exemplary embodiments of the present disclosure relate to a parking brake apparatus for a vehicle, and more particularly, to a parking brake apparatus for a vehicle capable of uniformly transmitting a load to a brake pad (brake pad).
Background
Generally, an actuator for an electronic parking brake system of a vehicle is constituted by an electric motor and a power transmission device for operating a friction plate mounted in a caliper of a disc brake device during parking.
When the driver pushes the parking brake switch, the rotational force of the motor of the actuator is transmitted to the input shaft of the caliper through a power transmission device such as a reduction gear. The pressure connection sleeve is moved forward by the rotation of the input shaft, and the caliper housing and the piston housing the pressure connection sleeve are moved toward each other by the forward movement of the pressure connection sleeve, so that two friction plates mounted to the piston and the caliper housing are pressed against both surfaces of the disc to restrain the rotation of the disc.
In the case where a plurality of pistons are provided and receive driving force from a single actuator, load may be unevenly transmitted to the plurality of pistons. In this case, uneven wear of the friction plate may be caused, and braking performance may be deteriorated.
Disclosure of Invention
Various embodiments relate to a parking brake apparatus for a vehicle capable of uniformly transmitting a load to a brake pad through a load transmitting unit (load transmission unit).
Further, various embodiments relate to a parking brake apparatus for a vehicle capable of selectively restricting rotation of a transmission gear member by a transmission gear member restricting unit, thereby selectively controlling a load balancing operation of a piston member.
In one embodiment, a parking brake apparatus for a vehicle may include: a motor section (motor section) that receives electric power from outside and generates power; a power transmission member rotated by driving of the motor member; a pair of pressing units that receive power from the power transmission member and press the brake pads; a load transfer unit that is installed between the pair of pressing units, is connected to each of the pair of pressing units, and transfers a pressing load of any one of the pair of pressing units to the other pressing unit; and a transmission gear member restraining unit that selectively restrains driving of the load transmission unit in conjunction with rotation of the power transmission member.
Each of the pair of pressing units may include: a sun gear member rotated by power received from the power transmission member; a planetary gear member rotated by meshing with the sun gear member; a carrier member coupled to the planetary gear member; and a piston member connected to the carrier member and moved toward the brake pad by receiving rotational power from the planetary gear member, thereby pressing the brake pad.
The power transmission member may include a small diameter transmission gear rotated by driving of the motor member, transmitting power to the sun gear member through a connection gear member, and coupled to the transmission gear member restraining unit.
The small-diameter transmission gear and the connection gear part may be formed in the shape of a helical gear, and the small-diameter transmission gear may move the transmission gear part restraining unit by moving relative to the connection gear part upon rotation.
The connecting gear member may include: a connecting gear body coupled to the sun gear member; a fifth wheel formed on an outer circumferential surface of the connecting gear body, meshed with the small-diameter transmission gear, and formed in a shape of a helical gear; and a connection insertion portion formed in a space of an inside of a wall on which the fifth wheel is formed, and in which a ring gear member is inserted.
The load transfer unit may include: a pair of ring gear members; and one or more transmission gear members disposed between and in meshing engagement with the pair of ring gear members.
Each of the pair of ring gear members may comprise: a ring gear inside having an internal gear portion formed on an inner peripheral surface thereof to mesh with the planetary gear members; and a ring gear outer coupled to an outer surface of the ring gear inner, and having an outer gear portion formed on an outer peripheral surface thereof to be engaged with the transmission gear member.
The transmission gear member restraining unit may include: a restraining body provided to face the transmission gear member and having a mounting hole portion into which the small-diameter transmission gear is mounted; and an anti-rotation engagement portion provided on the constraint body and formed to engage with the transmission gear engagement portion of the transmission gear member.
The anti-rotation engagement portion and the transmission gear engagement portion may be formed in a zigzag shape to be engaged with each other.
The rotation of the drive gear member may be constrained when the anti-rotation engagement and the drive gear engagement are engaged and the rotation of the drive gear member may be allowed when the anti-rotation engagement and the drive gear engagement are not engaged.
The parking brake apparatus may further include: and a constraint maintaining unit that supplies a pressing force to the transmission gear member constraint unit to maintain a state in which the transmission gear member constraint unit is engaged with the transmission gear member.
The power transmission member may further include: a first transfer gear engaged with the motor member and receiving power from the motor member; a second transmission gear connected to the first transmission gear, having a smaller diameter than the first transmission gear, and rotating in the same direction as the first transmission gear; and a large diameter transmission gear engaged with the second transmission gear, wherein the small diameter transmission gear is connected to the large diameter transmission gear, has a smaller diameter than the large diameter transmission gear, and rotates in the same direction as the large diameter transmission gear.
In the parking brake apparatus for a vehicle according to the present disclosure, when a pressing load is concentrated on any one of the plurality of pressing units, the load transmitting unit may transmit the pressing load to the remaining pressing units, such that the pressing units may press the brake pad with a uniform load.
Further, according to the present disclosure, the rotation of the transmission gear member is selectively restricted by the transmission gear member restricting unit such that the load balancing operation of the piston member can be performed when the braking operation is performed, and the load balancing operation of the piston member can be released when the braking operation is released.
Drawings
Fig. 1 is a perspective view illustrating a parking brake apparatus for a vehicle according to an embodiment of the present disclosure.
Fig. 2 is a partial perspective view illustrating a parking brake apparatus for a vehicle according to an embodiment of the present disclosure.
Fig. 3 and 4 are partial perspective views illustrating a driving unit, a power transmission member, a connection gear member, and a ring gear member in a parking brake device for a vehicle according to an embodiment of the present disclosure.
Fig. 5 and 6 are views showing coupling relationships of a driving unit, a power transmission member, a transmission gear member restraining unit, a transmission gear member, a connection gear member, and a ring gear member in a parking brake device for a vehicle according to an embodiment of the present disclosure.
Fig. 7 and 8 are views showing coupling relationships of a small-diameter transmission gear, a transmission gear member restraining unit, and a transmission gear member in a parking brake device for a vehicle according to an embodiment of the present disclosure.
Fig. 9 and 10 are views showing an unengaged state and an engaged state of a transmission gear member and a transmission gear member in a parking brake apparatus for a vehicle according to an embodiment of the present disclosure.
Fig. 11 is a front perspective view showing a coupling relationship of a driving unit, a power transmission member, a transmission gear member restraining unit, a transmission gear member, a connection gear member, and a ring gear member in a parking brake device for a vehicle according to an embodiment of the present disclosure.
Fig. 12 is a view showing a state in which a transmission gear member restraining unit and a transmission gear member are engaged in a parking brake device for a vehicle according to an embodiment of the present disclosure.
Fig. 13 is a view showing a state in which a transmission gear member restraining unit and a transmission gear member are not engaged in a parking brake device for a vehicle according to an embodiment of the present disclosure.
Fig. 14 is a partial front exploded view illustrating a parking brake apparatus for a vehicle according to an embodiment of the present disclosure.
Fig. 15 is a front view illustrating a parking brake apparatus for a vehicle according to an embodiment of the present disclosure.
Fig. 16 to 18 are state diagrams showing driving states of a parking brake device for a vehicle according to an embodiment of the present disclosure.
Fig. 19 is a partial rear exploded view illustrating a parking brake apparatus for a vehicle according to an embodiment of the present disclosure.
Detailed Description
Hereinafter, a parking brake device for a vehicle will be described below by way of a plurality of examples of embodiments with reference to the accompanying drawings. It should be noted that the figures are not to precise scale and that the thickness of the lines or the size of the elements may be exaggerated for descriptive convenience and clarity only.
Furthermore, the terms used herein are defined by considering the functions of the present invention, and may be changed according to the intention or practice of a user or operator. Accordingly, the terms should be defined in light of the entire disclosure set forth herein.
Fig. 1 is a perspective view showing a parking brake apparatus for a vehicle according to an embodiment of the present disclosure, fig. 2 is a partial perspective view showing a coupling relationship of a parking brake apparatus for a vehicle according to an embodiment of the present disclosure, fig. 3 and 4 are partial perspective views showing a driving unit, a power transmission member, a connection gear member, and a ring gear member in a parking brake apparatus for a vehicle according to an embodiment of the present disclosure, fig. 5 and 6 are views showing a coupling relationship of a driving unit, a power transmission member, a transmission gear member restraining unit, a transmission gear member, a connection gear member, and a ring gear member in a parking brake apparatus for a vehicle according to an embodiment of the present disclosure, fig. 7 and 8 are views showing a coupling relationship of a small-diameter transmission gear, a transmission gear member restraining unit, and a transmission gear member in a parking brake apparatus for a vehicle according to an embodiment of the present disclosure, fig. 9 and 10 are views showing a non-engaged state and an engaged state of a transmission gear member restraining unit and a transmission gear member in a parking brake apparatus for a vehicle according to an embodiment of the present disclosure, fig. 5 and 6 are views showing a coupling relationship of a driving unit, a transmission gear member, a transmission member, a connection gear member, and a ring gear member, a coupling relationship of a transmission member, and a parking brake member, a coupling relationship of a parking brake member, and a vehicle according to an embodiment of the present disclosure, and a parking brake member according to an embodiment of the present disclosure are shown, fig. 13 is a view showing a state in which a transmission gear member restraining unit and a transmission gear member are not engaged in a parking brake device for a vehicle according to an embodiment of the present disclosure, fig. 14 is a partial front exploded view showing the parking brake device for a vehicle according to an embodiment of the present disclosure, fig. 15 is a front view showing the parking brake device for a vehicle according to an embodiment of the present disclosure, fig. 16 to 18 are state diagrams showing a driving state of the parking brake device for a vehicle according to an embodiment of the present disclosure, and fig. 19 is a partial rear exploded view showing the parking brake device for a vehicle according to an embodiment of the present disclosure.
Referring to fig. 1 to 13, a parking brake apparatus 1 for a vehicle according to an embodiment of the present disclosure includes a driving unit, pressing units 100 and 200, and a load transfer unit 300.
The driving unit includes a motor part 30 that receives electric power from the outside and generates power. The motor part 30 includes a motor body 31 generating power and a driving gear 32 rotated by the motor body 31.
In the present embodiment, the driving gear 32 is formed in the shape of a worm wheel, and transmits power directly to the pressing units 100 and 200 or transmits power to the pressing units 100 and 200 through the power transmission member 40.
The drive unit includes a power transmission member 40. The motor part 30 of the driving unit may indirectly transmit the generated power to the pressing units 100 and 200 through the power transmission part 40.
The power transmission member 40 includes a first transmission gear 41 and a second transmission gear 42.
The first transfer gear 41 is engaged with the drive gear 32 and rotates with the rotation of the drive gear 32.
The second transmission gear 42 is connected to the first transmission gear 41, and rotates in the same direction as the first transmission gear 41 rotates.
In the present embodiment, the first transmission gear 41 and the second transmission gear 42 are integrally coupled with each other. Since the first transmission gears 41 have a larger diameter than the second transmission gears 42, their longitudinal sections have a T-shape.
The power transmission member 40 further includes a large diameter transmission gear 51 and a small diameter transmission gear 52.
The large diameter transmission gear 51 meshes with the second transmission gear 42 and rotates with the rotation of the second transmission gear 42.
The small diameter transmission gear 52 is connected to the large diameter transmission gear 51, and rotates in the same direction as the large diameter transmission gear 51 rotates. The small diameter transmission gear 52 is formed in the shape of a helical gear.
In the present embodiment, the large diameter transmission gear 51 and the small diameter transmission gear 52 are integrally coupled with each other. Since the large diameter transmission gears 51 have a larger diameter than the small diameter transmission gears 52, their longitudinal sections have a T-shape.
The parking brake apparatus 1 for a vehicle according to the present embodiment further includes a transmission gear member restraining unit 90.
The transmission gear member restraining unit 90 may selectively restrain the rotation of the transmission gear member 320. That is, in the case where the rotation of the transmission gear member 320 is not required, the rotation of the transmission gear member 320 may be restrained by the operation of the transmission gear member restraining unit 90.
The transmission gear member restraining unit 90 includes a restraining main body 91, an anti-rotation engaging portion 92, and a mounting hole portion 93.
The shape of the constraint body 91 does not interfere with the rotation of the connecting gear members 120 and 220 and the ring gear member 310.
In the present embodiment, the constraint body 91 is formed in a triangle shape and is disposed between the connecting gear member 120 and the connecting gear member 220 spaced apart from each other and between the ring gear member 310 and the ring gear member 310 spaced apart from each other.
Therefore, even if the constraint body 91 moves in conjunction with the movement of the small diameter transmission gear 52, the constraint body 91 does not collide with the connection gear members 120 and 220 and the ring gear member 310. Therefore, the constraint body 91 does not interfere with the rotation of the connecting gear members 120 and 220 and the ring gear member 310.
The rotation preventing engagement portion 92 is provided on the constraint body 91. An anti-rotation engagement portion 92 is formed on one surface of the constraint body 91 facing the transmission gear member 320 to prevent the transmission gear member 320 from rotating.
A mounting hole portion 93 is formed in the constraint body 91 to allow the small diameter transmission gear 52 to be mounted therein. The small diameter transmission gear 52 rotates by the rotation of the large diameter transmission gear 51, and transmits the rotational force to the connection gear members 120 and 220.
The small diameter transmission gear 52 is rotatably mounted in the mounting hole portion 93. When the small diameter transmission gear 52 is mounted in the mounting hole portion 93, the constraint body 91 moves in conjunction with the movement of the small diameter transmission gear 52.
The anti-rotation engagement portion 92 is formed to mesh with a transmission gear engagement portion 321 formed in the transmission gear member 320.
Each of the rotation preventing engaging portions 92 has projections and depressions alternately disposed toward the transmission gear member 320, and each of the transmission gear engaging portions 321 has projections and depressions alternately disposed toward the constraint body 91. In other words, the anti-rotation engagement portion 92 and the transmission gear engagement portion 321 are formed in a zigzag shape so as to be engaged with each other.
Because of this fact, since the projections and depressions of the anti-rotation engaging portion 92 and the projections and depressions of the transmission gear engaging portion 321 are engaged with each other, the anti-rotation engaging portion 92 and the transmission gear engaging portion 321 are engaged with each other.
With the anti-rotation engagement portion 92 and the transmission gear engagement portion 321 engaged, the rotation of the transmission gear member 320 is restricted by the transmission gear member restricting unit 90, i.e., is restricted by the transmission gear member restricting unit.
That is, the transmission gear member 320 cannot rotate in a state where the anti-rotation engagement portion 92 and the transmission gear engagement portion 321 are engaged, but can only rotate in a state where the anti-rotation engagement portion 92 and the transmission gear engagement portion 321 are not engaged.
In the case where the parking brake apparatus 1 for a vehicle is in a non-operating state, that is, in the case where a braking load is not applied, the transmission gear member restraining unit 90 is engaged with the transmission gear member 320. Accordingly, the rotation of the transmission gear member 320 is restrained by the transmission gear member restraining unit 90.
The parking brake apparatus 1 for a vehicle according to the present embodiment may further include a constraint maintaining unit 80.
The constraint maintaining unit 80 supplies a pressing force to the transmission gear member constraint unit 90 to maintain a state in which the transmission gear member constraint unit 90 is engaged with the transmission gear member 320.
The constraint maintaining unit 80 may directly supply the pressing force to the transmission gear member constraint unit 90, or may supply the pressing force through the large diameter transmission gear 51 or the small diameter transmission gear 52 integral with the transmission gear member constraint unit 90.
The present embodiment shows that the constraint maintaining unit 80 supplies the pressing force to the transmission gear member constraint unit 90 through the large diameter transmission gear 51.
The constraint maintaining unit 80 may include an elastic member. In a state where one end of the elastic member is fixed, the other end of the elastic member can provide a pressing force to the large diameter transmission gear 51 by an elastic restoring force.
Since the transmission gear member restraining unit 90 always provides the pressing force toward the transmission gear member 320 by the restraining maintaining unit 80, the coupling force between the anti-rotation engaging portion 92 and the transmission gear engaging portion 321 increases, which can prevent the engagement between the anti-rotation engaging portion 92 and the transmission gear engaging portion 321 from being released in a state where no separate external force is provided (see fig. 12).
The magnitude of the pressing force supplied from the constraint maintaining unit 80 to the transmission gear member constraint unit 90 is set smaller than the upward axial force (axial force in a direction away from the transmission gear member 320 in fig. 13) generated in the small-diameter transmission gear 52, as will be described later.
If an upward axial force is generated when the small-diameter transmission gear 52 rotates, the transmission gear member restraining unit 90 integral with the small-diameter transmission gear 52 moves together with the small-diameter transmission gear 52 while overcoming the pressing force of the restraint maintaining unit 80 (see fig. 13).
When the transmission gear member restraining unit 90 moves in a direction away from the transmission gear member 320, the engagement between the rotation preventing engagement portion 92 and the transmission gear engagement portion 321 is released, and thus the transmission gear member 320 is in a rotatable state.
In the case where the parking brake apparatus 1 for a vehicle is in an operating state, that is, in the case where a braking load is applied, the restriction of the rotation of the transmission gear member 320 is released by the upward axial force in the small diameter transmission gear 52, and thus the transmission gear member 320 becomes rotatable. Therefore, even when the pressing load is concentrated on any one of the plurality of pressing units 100 and 200, the pressing load can be transmitted to the remaining pressing units, so that the pressing units 100 and 200 can press the brake pad 20 with a uniform load.
In the case where the operation of the parking brake device 1 for a vehicle ends, that is, in the case where the brake load is removed, a downward axial force (axial force in the direction facing the transmission gear member 320 in fig. 13) is generated in the small-diameter transmission gear 52.
Due to this fact, the small diameter transmission gear 52 returns to the position of fig. 12, and the rotation of the transmission gear member 320 is prevented as the rotation preventing engagement portion 92 and the transmission gear engagement portion 321 are engaged.
In the case where the small-diameter transmission gear 52 is returned to the original position, the transmission gear member restraining unit 90 integral with the small-diameter transmission gear 52 may be engaged with the transmission gear member 320 by the pressing force of the restraining maintenance unit 80.
In the case of removing the braking load in the parking brake apparatus 1 for a vehicle, since the rotation of the transmission gear member 320 is prevented, the piston load balancing operation by the transmission gear member 320 is prevented.
Accordingly, during a braking operation of releasing the parking brake apparatus 1 for a vehicle, the respective piston members 170 and 270 are separated from the brake pad 20 without a separate load balancing operation, and thus a braking release operation can be performed in real time, whereby a braking release performance can be improved.
Referring to fig. 1, 2 and 14 to 19, a parking brake apparatus 1 for a vehicle according to the present embodiment includes a mounting housing 500 and a mounting cover 510.
The driving unit, the pressing units 100 and 200, and the load transmission unit 300 are disposed in the mounting case 500. The mounting cover 510 is detachably coupled to the mounting housing 500, and closes one side opening of the mounting housing 500 so as to prevent foreign objects from entering the inside of the mounting housing 500.
The pressing units 100 and 200 according to the present embodiment are installed in the caliper housing 10, receive power from the driving unit, and press the brake pads 20 in frictional contact with a disc (not shown).
A plurality of pressing units 100 and 200 are provided. The plurality of pressing units 100 and 200 are disposed side by side. These pressing units 100 and 200 are symmetrically installed at left and right sides with respect to a central portion of the brake pad 20 (fig. 15).
The pressing units 100 and 200 receive power from the driving unit and press the brake pad 20 with the same pressing load. The brake pad 20 is moved toward the disk by such pressing force, and braking force is generated due to friction between the brake pad 20 and the disk.
The pressing units 100 and 200 according to the present embodiment include sun gear members 110 and 210, connection gear members 120 and 220, planetary gear members 130 and 230, carrier members 150 and 250, and piston members 170 and 270.
Meanwhile, for convenience of explanation, the connection gear bodies 121 and 221 connecting the gear members 120 and 220 are omitted in the diagrams of fig. 15 to 18.
The connection gear members 120 and 220 include connection gear bodies 121 and 221, connection wheels 122 and 222, and connection insertion portions 123 and 223.
The connection gear members 120 and 220 include connection wheels 122 and 222 formed on outer peripheral surfaces thereof to be engaged with the driving unit (specifically, the small diameter transmission gear 52 of the power transmission member 40).
The power generated in the motor member 30 is transmitted to the fifth wheels 122 and 222 through the power transmission member 40. That is, the power of the motor part 30 is transmitted to the connection gear parts 120 and 220 to rotate the connection gear parts 120 and 220.
Like the small diameter drive gear 52, each of the fifth wheels 122 and 222 is formed in the shape of a helical gear.
The connection inserts 123 and 223 are formed in the space inside the fifth wheels 122 and 222. In other words, the fifth wheels 122 and 222 are formed on the outer sides of the walls formed on the outer circumferential surfaces of the connecting gear bodies 121 and 221, and the connecting inserts 123 and 223 are formed in the space inside the walls formed with the fifth wheels 122 and 222.
Ring gear member 310 (specifically, ring gear interior 311) is inserted into connection inserts 123 and 223. The connection insertion portions 123 and 223 are formed in the shape of grooves.
The sun gear members 110 and 210 are rotated by receiving power from the driving unit. According to the present embodiment, sun gear members 110 and 210 are coupled to connecting gear members 120 and 220. The sun gear members 110 and 210 may be rotated by connecting gear members 120 and 220 that are dynamically connected to the drive unit.
The sun gear members 110 and 210 include sun gears 111 and 211 and sun gear connecting bodies 112 and 212.
The sun gear connecting bodies 112 and 212 are coupled to the connecting gear bodies 121 and 221. The sun gears 111 and 211 are formed at central portions of the sun gear connecting bodies 112 and 212, and have outer peripheral surfaces formed in a gear shape to mesh with the planetary gear members 130 and 230.
The center of rotation of sun gear members 110 and 210 is concentric with the center of rotation of connecting gear members 120 and 220. In the case where power is transmitted from the power transmission member 40 to the connection gear members 120 and 220, the connection gear members 120 and 220 and the sun gear members 110 and 210 rotate about the same rotation axis.
The sun gear members 110 and 210 are disposed inside the inner peripheral surfaces of the connection gear members 120 and 220, on which connection inserts 123 and 223 are formed.
The sun gear members 110 and 210 may be integrally formed with the connecting gear members 120 and 220. Alternatively, the sun gear members 110 and 210 may be formed as separate bodies from the connection gear members 120 and 220, and may be integral with the connection gear members 120 and 220 by coupling.
Since the sun gear members 110 and 210 are integrally formed with the connection gear members 120 and 220 or with the connection gear members 120 and 220, in the case where the connection gear members 120 and 220 driven by the power received from the power transmission member 40 are rotated, the sun gear members 110 and 210 are also rotated together.
Sun gears 111 and 211 are disposed inside planetary gear members 130 and 230, respectively, each of which is provided with a plurality of gears. The planetary gear members 130 and 230 rotate and revolve while being meshed with the sun gears 111 and 211.
The planetary gear members 130 and 230 include a plurality of planetary gears 131 and 231. The present embodiment shows that the number of the planetary gears 131 and 231 is each illustrated as four. However, it should be noted that the present embodiment is not limited thereto, and thus the number of the planetary gears 131 and 231 may each be three or less or five or more.
The plurality of planetary gears 131 and 231 are disposed at equal angles around the rotation centers of the sun gears 111 and 211. The plurality of planetary gears 131 and 231 are engaged with the sun gears 111 and 211, and rotate and/or revolve when the sun gears 111 and 211 rotate.
The planetary gear members 130 and 230 are coupled to carrier members 150 and 250. In the case where the plurality of planetary gears 131 and 231 revolve around the sun gears 111 and 211, the carrier members 150 and 250 also rotate in the clockwise or counterclockwise direction (fig. 15).
As the bracket members 150 and 250 rotate, the piston members 170 and 270 move toward the brake pad 20 and press the brake pad 20.
The bracket parts 150 and 250 include bracket bodies 151 and 251, bracket rotation shafts 152 and 252, and bracket connection parts 153 and 253.
The carrier rotation shafts 152 and 252 are formed on the carrier bodies 151 and 251 to protrude toward the planetary gear members 130 and 230.
The number of carrier rotation shafts 152 and 252 is set to be the same as the number of the planetary gears 131 and 231 of the planetary gear members 130 and 230, and is coupled through the planetary gears 131 and 231 of the planetary gear members 130 and 230. Due to this fact, the planetary gears 131 and 231 of the planetary gear members 130 and 230 can perform a rotational motion during rotation on the carrier rotational shafts 152 and 252.
The bracket connection portions 153 and 253 are formed on inner circumferential surfaces of the bracket main bodies 151 and 251, and are connected to the piston connection portions 173 and 273 of the piston members 170 and 270.
In the present embodiment, the bracket connection parts 153 and 253 have a groove shape, and the piston connection parts 173 and 273 have a protrusion shape, which are inserted into the bracket connection parts 153 and 253, respectively.
Alternatively, the piston connecting portions 173 and 273 may have a shape of a groove, and the bracket connecting portions 153 and 253 may have a shape of a protrusion, which are inserted into the piston connecting portions 173 and 273, respectively.
The bracket connection portions 153 and 253 and the piston connection portions 173 and 273 may be coupled to each other with splines. Of course, the bracket members 150 and 250 and the piston members 170 and 270 may be coupled in other ways than a spline coupling, such as a threaded coupling, etc.
The piston members 170 and 270 are coupled with the bracket members 150 and 250. The piston members 170 and 270 rotate with the rotation of the bracket members 150 and 250.
The piston members 170 and 270 include piston bodies 171 and 271, piston shafts 172 and 272, and piston connecting portions 173 and 273.
The piston main bodies 171 and 271 are formed to be hollow in the inside and are disposed to be capable of coming into contact with the brake pad 20 by movement thereof. The piston main bodies 171 and 271 may be formed in a cylindrical shape.
The piston main bodies 171 and 271 are coupled with the piston shafts 172 and 272, and the piston connecting portions 173 and 273 are formed at one ends of the piston shafts 172 and 272 (i.e., the ends of the piston shafts 172 and 272 facing the bracket members 150 and 250).
As the bracket parts 150 and 250 rotate, the piston connections 173 and 273, which are splined to the bracket connections 153 and 253, rotate, and thus the rotational movement of the bracket parts 150 and 250 is converted into the linear movement of the piston parts 170 and 270.
Due to the linear movement of the piston members 170 and 270, the piston members 170 and 270 move toward the brake pad 20. Accordingly, when the piston members 170 and 270 contact the brake pad 20 and press the brake pad 20, braking force is generated due to friction between the brake pad 20 and the disc.
The load transfer unit 300 is connected to each of the pair of pressing units 100 and 200, and transfers the pressing load of any one of the pressing units 100 and 200 to the other of the pressing units 100 and 200.
The load transfer unit 300 according to the present embodiment includes a pair of ring gear members 310 and one or more transmission gear members 320.
A pair of ring gear members 310 are rotatable by meshing engagement with planetary gear members 130 and 230, respectively.
Alternatively, the pair of ring gear members 310 may be indirectly engaged through an intermediate one or more transfer gear members 320. That is, the transfer gear member 320 may be disposed between the pair of ring gear members 310 and meshed with the pair of ring gear members 310.
Referring to fig. 14-18, a respective ring gear member 310 may be mounted between the planetary gears 131 and 231 and the fifth wheels 122 and 222.
Each ring gear member 310 includes a ring gear inner 311 and a ring gear outer 315.
The ring gear inner 311 is provided outside the planetary gear members 130 and 230, and an internal gear portion 312 may be formed on an inner peripheral surface of the ring gear inner 311 to mesh with the planetary gear members 130 and 230.
The inner gear portion 312 of the ring gear inner 311 mounted at one side (left side in fig. 16) meshes with the planetary gear member 130 to rotate in a clockwise or counterclockwise direction (fig. 16), and transmits power to the ring gear member 310 provided at the other side (right side in fig. 16), specifically, the ring gear outer 315, through the transmission gear member 320.
The ring gear outer 315 is coupled to an outer surface of the ring gear inner 311, and an outer gear portion 316 is formed on an outer peripheral surface of the ring gear outer 315 to mesh with the transmission gear member 320. The ring gear outer 315 may be integrally formed with the ring gear inner 311.
When the internal gear portion 312 of the ring gear inner 311 mounted at one side (left side in fig. 16) rotates while meshing with the planetary gear member 130, the ring gear outer 315 integrally formed with the ring gear inner 311 also rotates in the same direction.
Accordingly, the rotational force of the ring gear outer 315 at one side is transmitted to the ring gear member 310 provided at the other side (right side in fig. 16), specifically, the ring gear outer 315, through the transmission gear member 320.
The transmission gear member 320 rotates by meshing with an external gear portion 316 formed on the ring gear member 310 (specifically, the ring gear outer 315) and transmits the rotational power of the ring gear member 310 provided at one side to the ring gear member 310 provided at the other side.
The rotational power transmitted to the ring gear member 310 at the other side is transmitted to the carrier member 250 coupled to the planetary gears 231 via the ring gear interior 311 and the planetary gears 231. As the planetary gear 231 rotates and revolves on the outer circumferential surface of the sun gear 211, the carrier member 250 coupled to the planetary gear 231 rotates, and thus, the piston member 270 moves toward the brake pad 20.
In the case where the pressing load for pressing the brake pad 20 is unevenly applied to the pair of pressing units 100 and 200 (specifically, the pair of piston members 170 and 270), the load transfer unit 300 may transfer the pressing load of the piston member 170 at one side to the piston member 270 at the other side, so that the pair of piston members 170 and 270 may be in contact with the brake pad 20 with the even pressing load.
Of course, conversely, the pressing load of the piston member 270 at the other side may be transmitted to the piston member 170 at one side.
Referring to fig. 15 to 18, in the present embodiment, the transmission gear member 320 is formed in the shape of a spur gear and rotates by meshing with the outer gear portion 316 formed on the outer peripheral surface of the ring gear outer 315.
However, the shape of the transmission gear member 320 may be replaced with various shapes other than the shape of a spur gear, such as a shape of a helical gear and a shape of a bevel gear in which the gear teeth of the gears are inclined at a predetermined angle with respect to the rotation axis of the transmission gear member 320.
Further, while the transmission gear member 320 is shown to have a gear shape, it should be noted that the present disclosure is not limited thereto, and various modifications may be made as if the following configurations were made: wherein the transmission gear member 320 is connected to the pair of ring gear members 310 in a belt shape and transmits power of the pressing unit 100 at one side to the pressing unit 200 at the other side.
The number of ring gear members 310 of the load transfer unit 300 may vary. Therefore, the number of ring gear members 310 is not limited to two in the present embodiment, and the number of ring gear members may be variously changed to one or three or more according to the distance between the pair of pressing units 100 and 200.
The operating principle of the parking brake apparatus 1 for a vehicle constructed as mentioned above will be described below.
In the parking brake apparatus 1 for a vehicle according to the embodiment of the present disclosure, the plurality of pressing units 100 and 200 press the brake pad 20 to move the brake pad 20 toward the disc, thereby generating braking force due to contact friction between the brake pad 20 and the disc.
In the embodiment of the present disclosure, two pressing units 100 and 200 are provided. However, it should be noted that the present disclosure is not limited thereto, and various modifications may be made, such as three or more pressing units.
When the parking brake apparatus 1 for a vehicle is operated, i.e., when a braking load is applied, the pressing units 100 and 200 receive power from the driving unit and reciprocate linearly with respect to the brake pad 20.
In detail, when power is generated in the motor part 30 by electric power received from the outside, the power transmission part 40 connected to the motor part 30 is rotated by the power received from the motor part 30. The power transmission member 40 transmits the rotational power to the pair of pressing units 100 and 200 at the same time.
In detail, the power generated from the motor main body 31 is transmitted to the first transmission gear 41 engaged with the driving gear 32. Since the second transmission gear 42 is connected to the first transmission gear 41, the second transmission gear 42 rotates in the same direction as the first transmission gear 41.
The rotational force of the second transmission gear 42 is transmitted to the large diameter transmission gear 51. Since the small diameter transmission gear 52 is connected to the large diameter transmission gear 51, the small diameter transmission gear 52 rotates in the same direction as the large diameter transmission gear 51.
The small diameter transmission gear 52 is constituted by a helical gear, and the connecting gear members 120 and 220 that mesh with the small diameter transmission gear 52 are also constituted by helical gears.
When the connection gear members 120 and 220 rotate with the rotation of the small diameter transmission gear 52, an upward axial force is generated in the small diameter transmission gear 52, and thus the small diameter transmission gear 52 moves in a direction away from the transmission gear member 320 (see fig. 13).
In the case where the parking brake apparatus 1 for a vehicle is in a non-operating state, that is, in the case where a braking load is not applied, the transmission gear member restraining unit 90 is engaged with the transmission gear member 320. Accordingly, the rotation of the transmission gear member 320 is restrained by the transmission gear member restraining unit 90.
Since the small-diameter transmission gear 52 and the connection gear members 120 and 220 are constituted by helical gears and the connection gear members 120 and 220 are fixed in their positions, an upward axial force generated in the small-diameter transmission gear 52 (i.e., an upward axial force is generated between the small-diameter transmission gear 52 and the connection gear members 120 and 220), which causes the small-diameter transmission gear 52 to move relative to the connection gear members 120 and 220.
In the case of power being supplied by the operation of the driving unit and the power transmission member 40, the engagement of the transmission gear member restraining unit 90 with the transmission gear member 320 is released by the upward axial force generated in the small-diameter transmission gear 52, and the transmission gear member 320 is in a rotatable state.
Since the first and second transmission gears 41 and 42 and then the large diameter transmission gear 51 and the small diameter transmission gear 52 are sequentially rotated by the driving of the motor part 30, the connection gear parts 120 and 220 engaged with the small diameter transmission gear 52 are rotated.
According to the rotation of the connection gear members 120 and 220, the sun gear members 110 and 210 also rotate in an interlocking manner, and the planetary gears 131 and 231 engaged with the sun gears 111 and 211 perform rotational movement while performing revolution movement around the sun gears 111 and 211.
When the planetary gears 131 and 231 perform the revolution motion, the carrier members 150 and 250 coupled to the planetary gears 131 and 231 are rotated in the clockwise or counterclockwise direction. As the bracket members 150 and 250 rotate, the piston members 170 and 270 coupled to the bracket members 150 and 250 move toward the brake pad 20 and press the brake pad 20 by contacting the brake pad 20.
The power supplied from the driving unit may be more transferred to any one of the pair of pressing units 100 and 200 due to various factors.
As shown in fig. 17, when the parking brake apparatus 1 for a vehicle is driven, in the case where the power transmitted to the pressing unit 100 provided at one side (left side in fig. 17) is greater than the power transmitted to the pressing unit 200 provided at the other side (right side in fig. 17), the piston member 170 at one side may be brought into contact with the brake pad 20 prior to the piston member 270 at the other side.
The planetary gear part 130 of the pressing unit 100 at one side performs only a rotational movement if the piston part 170 at the other side is in a state in which it has been in contact with the brake pad 20 and the piston part 270 at the other side is in a state in which it has not been in contact with the brake pad 20. That is, the planetary gear member 130 does not perform the revolution motion.
Since power generated by the operation of the driving unit is continuously transmitted to the sun gear 111, the sun gear 111 continuously rotates. At this time, since the piston member 170 is in a state in which it has been in contact with the brake pad 20, the plurality of planetary gears 131 engaged with the sun gear 111 do not perform revolution operation, but only perform rotational movement.
After the pressing unit 100 (specifically, the piston member 170) provided at the left side of fig. 17 is no longer movable toward the brake pad 20, the planetary gear 131 performs only a rotational movement due to a reaction force thereto, and the ring gear inner 311 formed with the internal gear portion 312 engaged with the planetary gear 131 rotates in a clockwise or counterclockwise direction.
By the ring gear outer 315 integrally coupled with the ring gear inner 311, a reaction force generated in the pressing unit 100 at one side (left side in fig. 17) is transmitted to the pressing unit 200 at the other side (right side in fig. 17) through the transmission gear member 320.
When the parking brake apparatus 1 for a vehicle is operated, that is, when a braking load is applied, the engagement of the transmission gear member restraining unit 90 and the transmission gear member 320 is released, and thus the transmission gear member 320 is in a rotatable state. Accordingly, the reaction force generated in the pressing unit 100 at one side can be transmitted to the pressing unit 200 at the other side through the transmission gear member 320.
The power supplied to the pressing unit 100 at one side is transmitted to the piston member 270 at the other side through the outer gear portion 316 at the other side, the inner gear portion 312 of the ring gear inner 311, the planetary gear member 230, and the carrier member 250 coupled with the planetary gear member 230.
Thus, the power supplied from the driving unit is supplied to the piston member 270 at the other side that has not been in contact with the brake pad 20, and the linear movement of the piston member 170 at the one side that has been in contact with the brake pad 20 is stopped until the piston member 270 at the other side is in contact with the brake pad 20.
Thereafter, when the piston member 170 at one side and the piston member 270 at the other side are both in contact with the brake pad 20, power of the driving unit is supplied to the respective piston member 170 at one side and piston member 270 at the other side, and the piston member 170 at one side and piston member 270 at the other side simultaneously press the brake pad 20 with a uniform load.
Referring to fig. 15 to 18, in the case where a pressing load is concentrated on the pressing unit 100 at one side between the pair of pressing units 100 and 200, the load transfer unit 300 according to an embodiment of the present disclosure may transfer the pressing load to the pressing unit 200 at the other side, such that the pair of pressing units 100 and 200 may press the brake pad 20 toward the disc with a uniform pressing load.
Also, in the case where the pressing load is more concentrated on the pressing unit 200 at the other side between the pair of pressing units 100 and 200, the load transmitting unit 300 may transmit the pressing load to the pressing unit 100 at one side, such that the pair of pressing units 100 and 200 may press the brake pad 20 toward the disc with a uniform pressing load.
Referring to fig. 14, the ring gear inner 311 may protrude more toward the sun gear members 110 and 210 (left side in fig. 14) than the ring gear outer 315, and may be inserted into the connection insertion portions 123 and 223 of the connection gear members 120 and 220.
Due to this fact, when receiving rotational power from the drive unit, the ring gear member 310 can be prevented from being released from the connection gear members 120 and 220 or the sun gear members 110 and 220.
When the bracket parts 150 and 250 are spline-coupled to the piston parts 170 and 270, the rotational power of the bracket parts 150 and 250 may be transmitted to the piston parts 170 and 270, specifically, the piston connection parts 173 and 273.
The piston connecting portions 173 and 273 are coupled to piston shafts 172 and 272 which are coupled to the piston bodies 171 and 271 and linearly move the piston bodies 171 and 271 toward the brake pad 20 via rotational power received through the bracket members 150 and 250.
In the case where the braking operation of the parking brake device 1 for a vehicle is released, that is, in the case where the braking load is removed, a downward axial force is generated in the small-diameter transmission gear 52, thereby moving the small-diameter transmission gear 52 toward the transmission gear member 320 (see fig. 12).
Accordingly, the transmission gear member restraining unit 90 and the transmission gear member 320 are engaged with each other, and restrain the rotation of the transmission gear member 320. Accordingly, the piston load balancing operation performed by the rotation of the transmission gear member 320 is prevented.
According to the present embodiment, during the brake operation of the parking brake apparatus 1 for a vehicle being released, the respective piston members 170 and 270 are separated from the brake pad 20 without a separate load balancing operation, and thus the brake release operation can be performed in real time, so that the brake release performance can be improved.
Although the present disclosure has been disclosed with reference to the embodiments shown in the drawings, these embodiments are for illustrative purposes only and it will be appreciated by those skilled in the art that various modifications and other equivalent embodiments may be made without departing from the scope and spirit of the disclosure, as defined in the claims. Therefore, the true technical scope of the present disclosure should be defined by the claims.

Claims (11)

1. A parking brake apparatus for a vehicle, comprising:
a motor part for generating power;
a power transmission member rotated by driving of the motor member;
a pair of pressing units that receive power from the power transmission member and press the brake pads;
A load transfer unit that is installed between the pair of pressing units, is connected to each of the pair of pressing units, and transfers a pressing load of any one of the pair of pressing units to the other pressing unit; and
a transmission gear member restraining unit that selectively restrains driving of the load transmission unit in conjunction with rotation of the power transmission member;
wherein the power transmission member includes a small diameter transmission gear that rotates by driving of the motor member, transmits power to the sun gear member of the pressing unit through a connection gear member, and is coupled to the transmission gear member restraining unit.
2. The parking brake device for a vehicle according to claim 1, wherein each of the pair of pressing units includes:
the sun gear member rotates by receiving power from the power transmission member;
a planetary gear member rotated by meshing with the sun gear member;
a carrier member coupled to the planetary gear member; and
a piston member connected to the carrier member and moved toward the brake pad by receiving rotational power from the planetary gear member, thereby pressing the brake pad.
3. The parking brake device for a vehicle according to claim 2,
wherein the small diameter transmission gear and the connecting gear member are formed in the shape of a helical gear, and
wherein the small diameter transmission gear moves the transmission gear member restraining unit by moving relative to the connecting gear member upon rotation.
4. A parking brake apparatus for a vehicle according to claim 3, wherein the connecting gear member includes:
a connecting gear body coupled to the sun gear member;
a fifth wheel formed on an outer circumferential surface of the connecting gear body, meshed with the small-diameter transmission gear, and formed in a shape of a helical gear; and
a connection insertion portion formed in a space of an inside of a wall on which the fifth wheel is formed, and in which a ring gear member is inserted.
5. The parking brake device for a vehicle according to claim 4, wherein the load transfer unit includes:
a pair of ring gear members; and
one or more transmission gear members disposed between and in meshing engagement with the pair of ring gear members.
6. The parking brake device for a vehicle according to claim 5, wherein each of the pair of ring gear members includes:
a ring gear inside having an internal gear portion formed on an inner peripheral surface thereof to mesh with the planetary gear members; and
a ring gear outer portion coupled to an outer surface of the ring gear inner portion, and an outer gear portion formed on an outer peripheral surface of the ring gear outer portion to mesh with the transmission gear member.
7. The parking brake device for a vehicle according to claim 5, wherein the transmission gear member restraining unit includes:
a restraining body provided to face the transmission gear member and having a mounting hole portion into which the small-diameter transmission gear is mounted; and
an anti-rotation engagement portion is provided on the restraining body and is formed to mesh with a transmission gear engagement portion of the transmission gear member.
8. The parking brake device for a vehicle according to claim 7, wherein the anti-rotation engagement portion and the transmission gear engagement portion are formed in a zigzag shape to be engaged with each other.
9. The parking brake apparatus for a vehicle according to claim 8, wherein rotation of the transmission gear member is restrained when the anti-rotation engagement portion and the transmission gear engagement portion are engaged, and rotation of the transmission gear member is permitted when the anti-rotation engagement portion and the transmission gear engagement portion are not engaged.
10. The parking brake device for a vehicle according to claim 7, further comprising:
and a constraint maintaining unit that supplies a pressing force to the transmission gear member constraint unit to maintain a state in which the transmission gear member constraint unit is engaged with the transmission gear member.
11. The parking brake apparatus for a vehicle according to claim 7, wherein the power transmission member further includes:
a first transfer gear engaged with the motor member and receiving power from the motor member;
a second transmission gear connected to the first transmission gear, having a smaller diameter than the first transmission gear, and rotating in the same direction as the first transmission gear; and
a large-diameter transmission gear meshed with the second transmission gear,
Wherein the small diameter drive gear is connected to the large diameter drive gear, has a smaller diameter than the large diameter drive gear, and rotates in the same direction as the large diameter drive gear.
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